Fully automatic power operated can opener



May 31, 1966 R. E. M LEAN 3,253,334

FULLY AUTOMATIC POWER OPERATED CAN OPENER Filed Feb. 10, 1964 5 Sheets-Sheet 1 7/ L g; INVENTOR.

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May 31, 1966 R. E. M LEAN 3,253,334

FULLY AUTOMATIC POWER OPERATED CAN OPENER Filed Feb. 10, 1964 5 Sheets-Sheet 2 INVENTOR 54b Poherf 5 M6494 y 1, 1966 R. E. MOLE-AN 3,253,334

FULLY AUTOMATIC POWER OPERATED CAN OPENER Filed Feb. 10, 1964 5 Sheets-Sheet 5 INVENTOR Pabefif .E. MGL em? A TTOKN 5Y5.

May 31, 1966 R. E. M LEAN FULLY AUTOMATIC POWER OPERATED CAN OPENER Filed Feb. 10, 1964 5 Sheets-Sheet 4 lil INVENTOR. /?0b/7 .5. MoLea/y ar A7722 7. .r

R. E. M LEAN May 31, 1966 FULLY AUTOMATIC POWER OPERATED CAN OPENER 5 Sheets-Sheet 5 Filed Feb. 10, 1964 INVENTOR.

United States Patent Wee 3,253,334 FULLY AUTOMATIC POWER OPERATED CAN OPENER Robert E. McLean, Raytown, Mo., assignor to Rival Manufacturing Company, a corporation of Missouri Filed Feb. 10, 1964, Ser. No. 343,642 16 Claims. (Cl. 30-4) This invention relates generally to can openers and deals more particularly with improvements in power operated can openers.

The principal object of the present invention is to provide a fully automatic power operated can opener that efficiently performs all phases of the operation of opening a can, including mechanical piercing of the end of the can by power means and subsequent automatic shutoff of the source of power upon the completion of the severing of the end from the can. It is a special feature of the invention that only a single operating lever is required and that this lever requires little manual pressure for its displacement. In the use of the can opener of my invention, the opener is readied for reception of the can by depression of the operating lever and upon release of the pressure, all operations, including piercing, take place sequentially through to automatic shut-off. Removal of the can is effected by again momentarily depressing the lever.

Another object of the invention is to provide a power operated can opener of the character described with novel, substantially frictionless cutter carrying means that not only contribute to the efficiency of the automatic shut-off feature of the can opener after the end has been completely severed from the can, but also permit increase in the lateral spacing between the overlapping portions of the can feed wheel and the cutter wheel when necessary, such as when the thick side seam portion of the engaged can is passing between these two members.

Still another object of the invention is to provide a way for mounting the cutter carrying means and the can feed wheel support means so that stress or strain resulting from the piercing of the end of the can by the cutter wheel exerts no twisting action on the frame of the can opener.

Yet another object of the invention is to provide a novel supporting link for the can feed wheel and all parts mounted on the same shaft therewith, including a portion of the can piercing mechanism, that maintains the axis of the can feed wheel and said parts in exceptionally good alignment at all times and thereby not only improve the efficiency of the can opener, but also minimize friction between the moving operating parts to provide easier operation and longer life of the unit.

A further object of the invention is to provide means effective to maintain the can feed wheel in positive can cutting relationship with the cutter wheel subsequent to piercing until the aforementioned operating lever has been depressed by the user.

A further object of the present invention is to provide, in association with the last mentioned means, mechanism operable to effect control of the period of operation of the can opener and operable to cause automatic shut-off upon completion of lid severance.

Still another object of the invention is to provide a power operated can opener construction which lends itself readily to incorporation of the feed wheel and cutter wheel orientation and relationship disclosed and described in my copending application Serial No. 262,532, filed March 4, 1963, which has matured into Patent No. 3,165,830, granted January 19, 1965.

Other and further objects of the invention together with the features of novelty appurtenant thereto will appear in the course of the following description.

The accompanying drawings which form a part of the 3,253,334 Patented May 31, 1966 specification and are to be read in conjunction therewith and in which like reference numerals indicate like parts in the various views;

FIG. 1 is a fragmentary front view of a preferred embodiment of a can opener incorporating the invention, the usual decorative outer casing being omitted;

FIG. 2 is an enlarged top plan view of same;

FIG. 3 is a rear elevational view of same, the operating parts being shown substantially in the position assumed while a can is being opened by the device;

FIG. 4 is an enlarged sectional view taken generally on the line 44 of FIG. 1 in the direction of the arrows, the movable parts again being shown substantially in the position assumed while a can is being opened;

FIG. 5 is a sectional view taken along line 55 of FIG. 2 in the direction of the arrows;

FIG. 6 is a fragmentary elevational, somewhat schematic view illustrating the can release lever, the can feed wheel supporting link and the can piercing mechanism, the view being taken from immediately rearward of the vertical front frame plate of the can opener as indicated generally by line x-x in FIG. 2, and the parts being illustrated in the positions assumed upon completion of piercing of the end of an engaged can by the cutter wheel;

FIG. 7 is a view similar to that of FIG. 6 but showing the respective parts in the positions assumed when the can release lever has been pivoted to the position in which its knob is in its lowermost location;

FIG. 8 is a sectional view taken substantially along line 8-8 of FIG. 2 in the direction of the arrows;

FIG. 9 is a sectional view taken substantially along line 9-9 of FIG. 2 in the direction of the arrows;

FIG. 10 is a view similar to that of FIG. 6 but illustrating a modified arrangement;

FIG. 11 is a view similar to FIG. 7 and showing the modified arrangement with the parts in the positions described for FIG. 7.

Referring now to the drawings, the main structural support for the can opener comprises the base member 24} having secured at its forward end the upstanding plate-like vertical frame 21. The base and frame may be of any contour and so formed to match the internal design of a suitable decorative case (not shown) of the type normally found on commercially offered units.

The upright frame is apertured as at 21a to receive from the rear side. the cutter wheel 22 and the serrated feed wheel 23 and their respective mounting mechanisms.

Providing one of the main internal supporting elements for the operating mechanism is the stud or arbor 24, which extends from the rearward of the upright frame 21. The stud has the head portion 24a, which is hot-headed into the frame to securely anchor it thereto. As seen in FIG. 5, the stud 24- is provided with a large diameter portion 24b, which cooperates with the head to maintain the stud in perpendicular orientation with respect to the frame member, a centrally located groove 24c and a reduced diameter end portion 24d. Pivoted on the stud for limited swinging movement is what will be termed the can feed wheel drive shaft supporting link 25. As shown in FIGS. 4 and 5, the link 25 is bifurcated at that end adjacent the stud, thus providing the gap 25a. Referring to FIG. 6, the link is generally oblong in cross-sectional shape, and, as will be subsequently seen, has journalled therein near its other end the feed wheel shaft 26. As shown in FIG. 5, movement of the link 25 axially rearwardly on the stud 24 is prevented by engagement of a set collar 27 with the rearward side of the groove 24c earlier described. The set collar is maintained securely in place by the set screw 27a. A curved spring washer 28 and fiat shims 29 are interposed between the enlarged portion 24b of the stud J and the adjacent end face of the support link to resiliently maintain the link rearwardly against the set collar.

As earlier noted the can feed wheel shaft 26 is journalled in the link 25, the bearings therefor comprising the tubular bushings 30 and 31 press fitted or cast in a cylindrical bore b formed near the free end of link 25. It will be noted that the front bushing extends substantially forwardly of the front end face of the link'25 and that the rearward bushing 31 extends somewhat rearwardly of the rearward end face of the link. The can feed wheel drive shaft is, of course, rotatably supported in the bushings.

Cast or otherwise secured on the knurled portion 26a at the rearward end of the feed wheel shaft 26 is the spur gear 32. At the forward end, the shaft is provided with parallel flats 26b and a reduced diameter threaded portion 26c. Adjacent the threaded portion and circumscribing the shaft is the apertured disc 33. This disc, as shown in FIG. 4, is somewhat thicker than the length of the flats 2612. Also, the disc aperture is provided with parallel flats which match those of the shaft so the disc is keyed to the shaft for rotation therewith. The can feed wheel 23 is screwed onto the threaded portion 260 of the feed wheel shaft. A spacer 34 and the required number of shim washers 35 (FIG. 4) are interposed between the feed wheel and the disc. It will be noted that tightening of the can feed wheel 23 on the threaded portion of the shaft also tightens the disc 33 securely between the shoulders of the flats 26b and the spacer 34. Although all operating thrust is rear ward on the can feed wheel and all parts assembled therewith, a curved spring washer 36 and shim washers 37 (FIGS. 2 and 4) are interposed between the rearward end of the bushing 31 and the gear 32 to maintain resilient rearward seating of the disc 33 against the forward end of the bushing 30 at all times when the device is not being operated.

Up and down movement of the can feed wheel 23 is controlled through the medium of a toggle linkage comprising, as seen best in FIGS. 4, 6 and 7, the upper link 38 and lower link 39 pivotally interconnected by the rivet 40. As will subsequently be seen, the toggle connection is manually operated through the medium of a hand lever 41.

The upper toggle link 38 has a somewhat enlarged portion which is apertured as at 38a to 'rotatably encircle the forward bushing 30 for the feed wheel shaft. The link is held in substantially fixed longitudinal position on the bushing by a tubular spacer 38b abutting at one end the disc and at the other the encircling portion of the link. Preferably the spacer 38b is composed of nylon or like non-metallic material. The lower link '39 of the toggle is pivotally connected by pin 42 to the frame 21. The pin 42 thus serves as the stationary pivot axis for the toggle linkage. It will be noted, particularly from FIG. 4, that the lower link 39 is provided with the offset portion 39a to space the linkage rearwardly of other components of the operating mechanism so that it may operate without interference. As shown in FIG. 4, the pivotal opening 3% of the link 39 is preferably slightly elongated parallel with the length of the link, for a purpose to be later explained.

The toggle linkage is maintained in its normally straightened relationship, that is, with the centers of pin 42, pivot fastener or rivet and feed wheel shaft 26 on a straight line therethrough. This position is illustrated in FIG. 6. The straightening force is supplied by a strong tension spring 43 which is connected at one end as at 43a to the lower toggle link 39 and at its other end by a hook portion 43b to a stud 44 anchored to and extending rearwardly of the frame 21. The spring 43 has considerable strength and always urges the toggle linkage toward its fully extended position and in fact maintains it in such position at all times except when the lower link 39 is manually rotated by manipulation of the hand lever 41, as will be explained later. It will be observed that the lower link 39 of the toggle has a portion extending upwardly past the pivot fastener or rivet 40, which portion includes an ear 39a which prevents the toggle linkage from departing to the left, as viewed in FIG. 6, from the straightened out or fully extended position. In other words, the ear 39a engages the side of the upper toggle link 38 when the fully extended condition for the toggle is reached.

As can be seen best in FIGS. 6 and 7, the manual operating lever is generally L-shaped in plan and has at its outer end a knob 41a suitably formed for engagement with the fingers of an operator. The lever is mounted for pivotal movement on the pin 42, which also serves as the pivotal mounting for the lower link 39 of the toggle. To prevent wobble of the operating lever and toggle link, a spacer 45 is interposed between the former and the frame 21. i

The upward extending leg of the hand lever 41 is formed to cooperate with a pair of diametrically opposed studs or pins 46 which are secured to the rearward face of the disc 33. The disc, as we have earlier seen, is mounted on feed wheel shaft 26 to turn therewith. The portion 41b of the hand lever, hereinafter sometimes called the pawl portion, extends upwardly alongside the feed wheel shaft and normally bears against the cylindrical spacer 38b earlier described. The upstanding portion is provided with a notch 410 which is positioned to cooperate with the studs 46 on the disc. The relationship between the notch 41c and the edge surface 41d of the upper leg of the hand lever proceeding upwardly therefrom is such that when the pin is fully coincidental with the notch, the edge surface rests against the spacer 38b. The hand lever is biased in the counterclockwise direction, as viewed in FIGS. 6 and 7, by a tension spring 47 having the end 47a hooked through ,a suitable aperture in the body of the hand lever and the other end 47b hooked around a stud 48 anchored in and extending from the rearward side of the main frame 21. A rearwardly turned lug 412 is provided along the left hand edge of the operating lever and this is operable to engage the adjacent edge of the lower link member 39 when the hand lever is rotated in a clockwise direction. Obviously, clockwise rotation of the hand lever results in pivoting of the lower link member 39 with accompanying swinging of the upper link member 38 and pivoting of the main feed wheel carrying link member 25 to the relative positions illustrated in FIG. 7.

The power for rotating the can feed wheel during operation is supplied by an electric motor M. In the preferred embodiment, the motor is supported with its output shaft in prime in a vertical position, the output shaft terminating in a worm W at the upper end. The base of .the motor is supported on three triangularly located studs 49, and 51 (see FIG. 1) projecting rearwardly from the main frame 21. The head portions only of the studs are visible in FIG. 1, but it will be understood that they project horizontally rearwardly of the plate and are abutted by the forward side of the base of the motor. The motor is secured to these studs by screws 49a, 50a and 51a, respectively, which extend through corresponding apertures in the motor base and are threaded into the studs. For the purpose of simplicity, the electrical conductors to the motor have not been shown. It will be understood, however, that they are so connected as to place the normally open switch S (see FIG. 3) in series with the motor so that when the contacts 52, 53 are closed (which is the condition illustrated in FIG. 3), the motor is running and when they are separated, the motor is off. More will be said of the switch audits operating relationship in the combination at a later point herein.

The worm W of the motor drivingly engages a large diameter worm gear 54a which forms a part of a combination worm gear and pinion 54 rotatably journalled on the rearmost portion 24a" (FIG. 5) of the stud 24'. The combined worm gear and pinion is, in the preferred embodiment, retained on the stud 24 by the washer 55 and screw 56 threaded into the rear end of the stud. As can best be seen in FIG. 2, the teeth of the spur pinion 54b mesh with the teeth of the larger diameter spur gear 32 which is secured to the feed wheel drive shaft 26. It is important to note that since the axis of the intermediate gear 54 is coincidental with the pivot axis for the link 25 carrying the feed wheel drive shaft 26, the

link 25 can be pivoted Without changing the operating relationship between the gears 54b and 32. In other words, power can be continuously supplied to the feed Wheel shaft even though there may be displacement of the shaft due to pivoting of its carrying link 25 during operations.

Returning now to the upper end of the can opener, the cutter Wheel 22 is supported on a carrier structure which includes the carrier platform 57 arranged horizontally above the feed wheel carrier link 25 and having the downwardly turned front and rear flanges 57a and 57b, respectively. A block 58 is secured to the platform 57 as by rivets 59 (FIGS. 2 and 3). The block is provided with the cylindrical bore into which is press-fitted the arbor 60 which extends from the block forwardly and downwardly to and through the opening 21a in the frame. The cutter wheel 22 is journalled on a reduced diameter portion of the arbor and is retained thereon by the washer 61 and screw 62. The compound angle and position of the cutter wheel with respect to the feed wheel during operation is the same as that disclosed in my copending application Serial No. 262,532, filed March 4, 1963, which has matured into Patent No. 3,165,830, granted January 19, 1965, and, as all the details with respect to this feature can be acquired from such application and since they play no part in the present invention, no further description will be given.

The carrier platform 57 is supported for limited pivotal movement about an axis coinciding with the axis of the stud 63 anchored in and extending rearwardly from the frame 21 (see FIGS. 1 and 5). As best seen in FIGS. 2 and 5, the forward edge of the platform is provided with a downturned ear 570 which is journalled on the pin 63. The ear 570 is biased toward the frame 21 [by a coiled compression spring 64 encircling the pin 63 and hearing at one end against the car 570 and at the other against a washer 65 secured to the pin by the screw 66. The ear seats forwardly against the enlarged diameter portion 63a of the pin 63. The fit between the opening through ear 57c and pin 63 should not be a close one as a certain amount of wobble is desired for a purpose later to be explained.

The platform 57 is also provided with a rearwardly located downturned hinge ear 57d. A shoulder rivet 67 is anchored in this ear and pivoted on the shoulder rivet is the upper end of a brace link 68. The lower end of the brace link is apertured to fit over the reduced diameter portion 24d of the pivot stud 24 for the feed wheel carrier 25.

Referring now to FIGS. 2, 3 and 9, at that end of the carrier platform 57 opposite from its pivot support and on the forward side thereof, the downturned flange 57:: has anchored therein a shoulder rivet 69. Pivoted on this shoulder rivet is the upper end of an elongate vertically oriented control link 70, the lower end of the control link '70 is loosely connected with a shoulder stud 71 anchored in the front frame 21. The control link has an opening 75a in the lower end portion which loosely encircles the reduced diameter portion of the stud 71, this opening being vertically elongated for limited up and down movement of the control link relative to the stud. The link is retained on the stud by the washer 72 and screw 73. The connection, both at the upper end and lower end of the switch control link, should be slightly loose so as to permit a limited degree of wobble.

The control link 70 carries near its lower end a rearwardly projecting pin 74, so located as to underlie and engage the lower arm '75 of the switch S.

As can best be seen in PEG. 3, the switch in the preferred embodiment comprises a two arm switch having the upper arm '76 and the lower arm 75. The switch is so constructed that the lower arm is of resilient material and is normally bowed downwardly so as to separate the contacts 52, 53. Upon raising of the control link 70, the arm 75 can be brought upwardly so as to close the contacts. This is the position for the switch illustrated in the drawings and is the condition which obtains, during the piercing of the can lid and while the can lid is being severed from the can body, as will subsequently be seen. For the present it should be borne in mind that lowering of the control link with consequent lowering of the pin 74 will result in separation of the switch contacts and de-energization of the motor M.

It will be understood of course that other types of switches may be employed, the principal requirement being that whenever the control link is in its lowermost position, the switch will be open and when in its uppermost or raised position, the switch will be closed and the motor energized.

The carrier platform 57 is continuously .biased toward the down position for the control link 70 by means of a light tension spring 77, the upper end of which is hooked in an opening in the rear platform flange 57b. The lower end of this spring is hooked in an annular groove formed in the motor support stud 51. Care should be taken to locate this groove forwardly of the plane of the rear flange 57b of the platform so that not only does the spring pull downwardly on the platform, but also forwardly or toward the frame 21.

The proper spacing of the platform 57 at that end carrying the control link 70, with respect to the frame 21, is obtained by the arrangement now to be described and seen best in FIGS. 2 and 8. As shown, the cylindrical pin 78 disposed in a generally horizontal plane has one end movably seated in a frusto-conical recess 79 formed in a circular boss on the rear side of the frame 21. The pin is headed at its other end and adjacent the head is a shoulder sleeve 80, the main portion of which is loosely received inan oversized aperture formed in the rear flange 57b of the platform 57. The shoulder of the sleeve 86 engages the margin of the opening in the flange and the shoulder is yieldably maintained in contact therewith by a compression spring 82. The spring is retained centrally of the pin by a washer 83 which in turn is engaged by extruded stops 78a formed on the pin. The pin extends freely through an enlarged opening in the front platform flange 57a.

As is evident from FIGS. 2 and 4-, the can feed wheel and cutter wheel project forwardly beyond the plane of the face of the upright main frame 21. Located below the opening 21a and substantially directly below the feed wheel is a can guard 84 which serves to maintain the side wall of an engaged can at the desired orientation with respect to the face of the can feed wheel. The can guard 84 is an L-shaped piece, the horizontal leg of which projects through a suitable opening in the frame and the inside leg of which is secured to the frame by the rivet 85. A fixed, rim engaging guide 86 is located in position to engage the rim of a can. This guide cooperates with a resilient leaf spring guide 87 on the opposite side of the feed wheel. Resilient guide 87 exerts downward pressure on the rim of an engaged can as necessary to cause adequate penetration by the teeth of the can feed wheel in the under edge of the rim or flange of the can to assure the required traction for feeding of the can by the can feed wheel in respect to the overlying cutter wheel. The resilent can guide 87 is secured .to the frame 21 by rivet 88.

Operation (embodiment of FIGS. 19, inclusive) In describing the operation of the embodiment of the can opener disclosed in connection with FIGS. 1-9, in-

clusive, it will be assumed that the motor M and its switch S have been connected into an electrical circuit and that the switch is in its off position, i.e., with the contacts 52 and 53 separated. With no can in the opener, the carrier platform 57 would be rotated slightly counterclockwise from the position illustrated in FIG. 3, and as a result control link 70, rather than being in the elevated position of FIG. 9 will be displaced downwardly so that the upper edg rather than the lower edge, of opening 75a bears on the stud 71. Accordingly, the switch arm 75 would be separated from the arm 76, and the contacts open. The force of gravity plus the tension in spring 77 serve to yieldably maintain the platform and control link in the positions just described. This in fact is the normal quiescent or passive condition for these parts.

The normal position for the feed wheel carrier link 25, its associated toggle linkage including links 38 and 39 and the manual control lever 41 are shown in FIG. 6. In this position, the toggle linkage is fully extended with the ear 39a on the lower link in engagement with the side of the upper link 38, the spring 43 serving to hold the parts there. The feed wheel shaft 26 thus is in a position where the feed wheel 23 is overlapped slightly by the cutter wheel 22 as illustrated in FIG. 1.

To prepare the can opener for reception of a can, the operator applies downward pressure on the knob 41a of the operating lever, thus pivoting it clockwise as viewed in FIGS. 1 and 6, or counterclockwise as is viewed in FIG. 3. As the hand lever is rotated, the ear 41c intercepts the edge of the lower toggle link 39 and causes it to move along with the hand lever. Through the toggle linkage, the feed wheel carrier link member 25 is thus pivoted clockwise (as seen in FIG. 6) about its pivot axis and when fully depressed, the parts are in the relative positions illustrated in FIG. 7. Clockwise rotation and depression of the link 25 is limited by engagement of the feed wheel 23 and spacer 34 with the lower edge of the front opening 21a. In other words, the feed wheel is moved downwardly until it strikes the lower edge of the opening. In this position it is sufliciently separated from the cutter wheel as to permit the insertion between the feed wheel and cutter wheel of the top flange and adjacent lip portion of a can with the outside lower portion of the flange resting upon the teeth of the feed wheel.

Once the can is in the inserted position, the downward pressure on the hand lever can be removed. As the pressure is removed, springs 43 and 47 serve to return the toggle linkage and operating lever toward the position of FIG. 6. This of course causes the feed wheel to rise and the lid of the can will be brought into bearing engagement with the lowermost point on the cutter wheel 22.

The relative position of the toggle linkage, feed wheel shaft and operating lever at the time that the top of the can is engaged by the cutter is substantially intermediate the position illustrated respectively in FIGS. 6 and 7. In other words, the toggle linkage is not yet in its fully straightened or extended condition as illustrated in FIG. 6. The spring 43 is provided however with adequate strength that it will act through the toggle linkage to continue to raise the can against the cutter wheel and thus to pivot the cutter wheel carrier platform 57 clockwise from its normal passive position to the position illustrated in FIGS. 3 and 9. This pivoting of the cutter carrier platform occurs before the lid of the can has been pierced. Obviously, as the carrier is pivoted it lifts the control link 70 with it and, acting through pin 74, serves to close .the contacts 52 and 53 of switch S, thereby energizing the motor. The spring itself does not have sufiicient strength as to cause the cutter to pierce the can lid. Instead, piercing is achieved through the operating relationship between the pawl portion 41b of the operating lever and the pins 46 carried by the disc 33 as now to be described.

The energization of the motor serves to initiate ro-,

tation of the feed wheel drive shaft 26 and its associated disc 33. As earlier suggested, when the motor M starts, the hand lever 41 will be in a position intermediate those of FIGS. 6 and 7. The hand lever 41, particularly the pawl portion 41b thereof, is so formed that at this intermediate position, the notch 41c lies within the orbital path followed by the pins 46. Accordingly, following energization of the motor and when one of the pins 46 arrives at and engages in the notch 41c, the notch and pin will cooperate to force link 25 on up to the FIG. 6 position. This has the effect of driving the can upwardly against the cutter wheel so that the lid is penetrated by the cutter wheel. As the can is forced upwardly, it will be obvious that the toggle linkage 38 and 39 will follow. After the pawl portion 41b of the can release lever is in the FIG. 6 position, the disc 33 can continue to rotate without changing the elevation of the can feed wheel. The pins 46 strike against the surface 41d and when passing thereby, cause the lever 41 to shift slightly to permit passage. The notch 41c is so formed that when the hand lever is in the FIG. 6 position, the pins can move freely out of the notch. To permit the necessary limited movement of hand lever 41 to accommodate passage of the pins 46, the ear 41a is spaced away from the edge of the link 39. The straightened out toggle link mechanism comprised of the links 38 and 39 will maintain the can feed wheel at the proper severing elevation until such time as the knob 41a is again manually depressed.

The opening 3% (FIG. 4) is slightly elongated, as previously stated, to compensate for manufacturing tolerances. Accordingly, should either of the pins 46, in cooperation with the portion 41b of the lever 41, raise the can feed wheel 23 a few thousandths of an inch higher than required to permit straightening out of the toggle mechanism consisting of the links 38 and 39, there would be no interference to prevent it. Conversely, should the toggle mechanism consisting of the links 38 and 39 not be fully extended when engagement of either of the pins 46 with the portion 41b of the lever 41 has raised the can feed wheel to maximum, the toggle will be so nearly straightened out that tension of the spring 43, which has an exceptionally great mechanical advantage at this point, will complete straightening it out. Of course, the end of the can would already have'been pierced by the cutter wheel in either case.

The resistance afforded by the end of the can against cutting has an upward component of sufiicient value to overcome the hold down spring 77 and consequently, so long as the can lid remains unsevered, the carrier platform 57 will remain in the FIG. 3 position, that is, with the contacts 52 and 53 of switch S closed. However, as soon as the end has been completely sheared from the can, the spring and gravity forces urging the cutter wheel and its carrier downwardly are unopposed by any upward forces and consequently the carrier drops, carrying with it the control link 70 and causing the switch S to open. The motor M will thereupon stop.

It is important to note that rotation of the pins 46 carried by discs 33 is in the direction that any frictional traction between the pins and notch 410 will urge the pins into the notch instead of out of the notch.

The can opener can operate satisfactorily with only one pin 46 rather than two. However, use of two pins assures a shorter interval following starting for engagement of a pin with the notch 41c, thereby obtaining an earlier pierc- 0 ing of the end of the can by the cutter wheel.

The function of the can guides 86 and 87 and the can guard 84 has been earlier set forth. By referring to FIGS. 4 and 5, it should be seen that stress or strain resulting from piercing of the end of a can by the cutter wheel imparts no twisting action to the front frame 21. To best attain the automatic action of the can opener, it is of utmost importance that upward and downward movement of the cutter wheel by the forces causing same be as unimpeded as possible. It is for this reason that the cutter carrier platform 57 is supported for as friction-free movement as possible, referring particularly to the relatively wide spacing between the hinge ears 57c and 57d, use of the support link 68 and inclusion of the pin 78. Also the provision of the support link 68 in combination with the somewhat floating support for the elongate pin 78, sleeve 80 and spring 82 greatly contributes to the substantially frictionless action of the cutter carrier platform 57 when the thick vertical side seam of a conventional can passes between the overlapping face portions of the feed wheel and cutter wheel. It will be observed that the free end of the carrier platform can be displaced toward the frame 21 against the predetermined pressure of the spring 82, the sleeve 80 sliding on the pin 7 8 as necessary. Of course the opening in front flange 57a of the carrier is large enough to permit unimpeded free up and down movement of the free end of the carrier, as can also be seen in FIG. 8. In other words, the over-size aperture through which the sleeve 80 extends, coupled with the wobble mounting of the pin 78 in the recess 79, allows for such swinging.

When opening has been completed, and whenever else it is desired to remove the can from the opener, the hand lever is depressed to separate the feed wheel from the cutter wheel.

Modified construction (FIGS. 10 and 11) Referring now to FIGS. 10 and 11, these figures illustrate a modification of the invention which involves a change in the nature of the hand operating lever and pawl portion of the preceding embodiment. All parts of the can opener other than those set forth below remain the same. For example, the feed wheel shaft 26 is still carried by the main pivotal carrier member and a disc, like disc 33 of the preceding embodiment, is mounted on the feed wheel shaft and carries the pins 46. A toggle linkage including links 38 and 39 extends between the feed wheel shaft and the pivot 42, the latter of which is, as in the preceding embodiment, anchored in the main front frame.

In the modified structure, the can release lever 90 is constructed as a separate lever and has its own biasing spring 91. Spring 91 is hooked at one end around a stud 92 secured to the front frame of the can opener and at its other end to an appropriate aperture formed in a projecting nose portion 90a of the hand lever. A stop pin 93 serves to limit the counterclockwise rotation of the hand lever. A pawl 94 is constructed much the same as the pawl portion of the hand lever 41 in the preceding embodiment, except that it is separate from the hand lever. The pawl 94 is also pivoted on pin 42. For cooperation with the hand lever, there is provided on the lower edge an outturned ear 94a which is engaged by the hand lever on depression of same to effect rotation of the pawl and collapse of the toggle linkage. The pawl also includes the rearlwardly turned ear 94b which, as in the case of ear Me of the preceding embodiment, serves to engage the lower link 39 in response to rotation of the pawl member. Springs 43 and 47, respectively, are like those of the preceding embodiment, the former being connected with the lower link 39 and the latter with the separated pawl 94 of this embodiment.

The operation of the modified structure.is basically the same as that shown and described in connection with the preceding embodiment except that the pawl and hand lever can rotate on the pivot stud 42 independently within certain limitations and therefore, rotation of the pawl due to the orbital contact therewith by a pin when the link is in the FIG. 10 position, will not impart an oscillating motion to the hand lever. Still, however, the manual downward movement of the hand lever will be accompanied by shifting of the parts to the position illustrated in FIG. 11 so that the can opener can be prepared for inserting of a can as in the preceding embodiment.

From the foregoing description, it will be seen that this invention is one well adapted to attain all of the ends and objects hereinabove set forth together with iii other advantages which are obvious and which are inherent in the structure.

It will be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of the claims.

Since many possible embodiments may be made of the invention without departing from the scope thereof, it is to be understood that all matter herein set forth or shown in the accompanying drawings is to be interpreted as illustrative and not in a limiting sense.

. Having thus described my invention, I claim:

1. In a power operated can opener, the combination of an upright support frame, a cutter member supported from said frame and provided with a downwardly facing cutting edge, a-feed wheel carrier member pivoted to the frame for rocking movement about a substantially horizontal pivot axis, a feed wheel shaft journalledin said carrier member and having its axis spaced from and parallel with said pivot axis, a feed wheel secured to said shaft, said carrier member and pivot axis so located that rocking of the carrier member raises and lowers the feed wheel with respect to the cutter member between an upper can cutting position and a lower can receiving position, a motor, means drivingly connecting said motor with said feed wheel shaft, 21 pin member carried by and radially offset from said feed wheel shaft for orbital travel about said shaft, a pawl member pivotally connected with said frame, said pawl member having a pin engageable portion, and said pin member and pawl memher so located as to produce an upward thrust force on said carrier member in response to engagement of said pin member with said portion when said carrier member is below the said can cutting position.

2. The combination as in claim 1 wherein said pin engageable portion comprises a notch in the pawl member which, when the carrier member is in the upper can cutting position for the feed wheel, freely passes the pin member during the rotation of the latter about the feed wheel shaft.

3. The combination as in claim 1 including lever means connected with said pawl and operable to swing same to a position in which said pin engagealble portion is out of the path of said pin member.

4. The combination as in claim 3 including a toggle linkage interconnecting said carrier and frame and having a fully extended condition corresponding to the upper position for the feed wheel carrier member and a folded condition corresponding to the lower position therefor, said toggle linkage including stop means preventing it from moving on through the fully extended condition, and resilient means urging said toggle linkage toward said fully extended condition from the folded condition.

5. The combination as in claim 4 wherein said lever means aotuates said toggle linkage toward the folded condition.

6. In a power operated can opener, the combination of an upright support frame, a cutter member supported from said frame and provided with a downwardly facing cutting edge, a feed wheel carrier member pivoted to the frame for rocking movement about a substantially horizontal pivot axis, a feed wheel shaft journalled in said carrier member and having its axis spaced from and parallel with said pivot axis, a feed wheel secured to said shaft, said carrier member and pivot axis so located that rocking of the carrier member raises and lowers the feed wheel between an upper can cutting position and a lower can receiving position, resilient means biasing said carrier member toward the can cutting position, manual lever means connected with said carrier member and operable to swing said carrier member toward the can receiving condition so that a can flange can be engaged with said feed wheel, a motor, means drivingly connecting said motor with said shaft, a pawl member pivoted to said frame below said carrier member and extending upwardly toward the carrier member, a pin element carried by and radially offset from said shaft, said pawl member having a notch for engaging said pin and co-acting therewith to thrust said carrier member to said upper can cutting position from a position intermediate said upper and lower positions.

7. The combination as in claim 6 wherein said notch is so formed and located as to permit free passage of the pin therethrough when said carrier member is in said cutting position.

8. The combination as in claim 6 including a toggle linkage interconnecting said carrier member and frame and having a fully extended condition corresponding to the upper position for the feed wheel carrier member and a folded condition corresponding to the lower position therefor, said toggle linkage including stop means preventing it from moving through the fully extended condition in the direction opposite the folded condition, said resilient means. urging said toggle linkage toward said fully extended condition.

- 9. The combination as in claim 8 wherein said lever means actuates said toggle linkage toward the folded condition.

10. In a power operated can opener, the combination of a stationary support frame, a feed wheel carrier member pivoted to said frame, a feed wheel supported on said carrier member, the pivot axis of said carrier member so located that rocking of the carrier member raises and lowers the feed wheel between upper and lower limit positions, a cutter disposed to cooperate with the feed wheel for severing the lid from a can whenever the feed wheel is in the said upper limit position, cutter carrier means connected with said support frame and supporting said cutter for limited up and down movement between up and down positions for the cutter, means yieldably biasing the cutter carrier means toward the down position for the cutter, an electric motor, power transmission means between said motor and feed wheel operable to maintain a continuous drive connection between said motor and feed wheel during rocking of said carrier member, a toggle linkage anchored at one end to said support frame and connected at its other end to said feed wheel carrier member and moveable between an extended condition corresponding to the upper limit position for the feed wheel and a folded condition corresponding to said lower limit position for the feed wheel, resilient means biasing said toggle linkage toward said extended position, manually operable lever means connected with said toggle linkage and operable to fold said toggle linkage thereby to separate the feed wheel from the cutter for insertion of a can rim therebetween, motor control means operably connected with said cutter carrier means and operable to start said motor on upward movement of said cutter from the down position and to shut off the motor on return toward the down position for the cutter,

and cooperating pin and pawl thrust means operable, in response to rotation of said feed wheel, to pivot said feed wheel carrier member to the upper limit position for the feed wheel from a position therebelow.

11. The combination as in claim 10 wherein the paw portion of said thrust means is formed as part of said lever means.

12. The combination as in claim 10 wherein said cutter carrier means is supported for limited fore and aft movement relative to said frame whereby to permit passage between the cutter wheel and the feed wheel of a can seam.

13. The combination as in claim 12 including spring means resiliently biasing said cutter carrier means rearwardly with respect to said frame whereby to return the cutter toward the feed wheel after passage of the seam.

14. In a power operated can opener, the combination of an upright support frame, a horizontal shaft secured to and extending rearwardly of said frame, a feed wheel carrier member journalled on said shaft, a feed wheel supported by said carrier member and received through an opening in the frame, means for rocking said carrier member to move said feed wheel between upper and lower limit positions, a cutter disposed to cooperate with the feed wheel for severing the lid from a can whenever the feed wheel is in the said upper limit position, cutter carrier means connected with said support frame and supporting said cutter, said cutter extending through said opening in the frame adjacent the feed wheel and said cutter carrier means comprising a substantially horizontal cutter carrier member extending laterally across and above said shaft on the rear side of said frame, one side of one end of said cutter carrier member being pivotally connected with said frame on an axis parallel with said shaft, a support link spaced rearwardly from the frame and extending between said shaft and said carrier member, said support link being pivoted at its lower end on said shaft and pivotally connected at its upper end with said cutter carrier member, and means resiliently biasing said cutter carrier member toward a position in which the pivotal connection between said support link and said cutter carrier member is on an axis which coincides with the first mentioned axis.

15. The combination as in claim 14 including a pin extending rearwardly from said frame adjacent the other end of said cutter carrier member, and resilient means interconnecting the outer end of said pin and said carrier member and operable to yieldably resist movement of said other end of said cutter carrier member toward said frame.

16. The combination as in claim 15 wherein said pin is connected with said support frame by seating the end thereof adjacent the frame in a socket on the frame constructed to permit wobble of the pin in response to up and down movement of said other end of the cutter carrier member.

References Cited by the Examiner UNITED STATES PATENTS 2,158,319 5/1939 Bloomfield 309 2,498,441 2/1950 McLean 3015.5 2,827,691 3/1958 Harmanson 304 2,896,319 7/1959 Pinette 304 2,952,073 9/ 1960 Congdon 3015 X 3,060,566 10/1962 Herbig 30-4 3,060,568 10/1962 Nisenson 304 WILLIAM FELDMAN, Primary Examiner.

MICHAEL BALAS, M. C. KRUSE, Examiners. 

1. IN A POWER OPERATED CAN OPENER, THE COMBINATION OF AN UPRIGHT SUPPORT FRAME, A CUTTER MEMBER SUPPORTED FROM SAID FRAME AND PROVIDED WITH A DOWNWARDLY FACING CUTTING EDGE, A FEED WHEEL CARRIER MEMBER PIVOTED TO THE FRAME FOR ROCKING MOVEMENT ABOUT A SUBSTANTIALLY HORIZONTAL PIVOT AXIS, A FEED WHEEL SHAFT JOURNALLED IN SAID CARRIER MEMBER AND HAVING ITS AXIS SPACED FROM AND PARALLEL WITH SAID PIVOT AXIS, A FEED WHEEL SECURED TO SAID SHAFT, SAID CARRIER MEMBER AND PIVOT AXIS SO LOCATED THAT ROCKING OF THE CARRIER MEMBER RASISES AND LOWERS THE FEED WHEEL WITH RESPECT TO THE CUTTER MEMBER BETWEEN AN UPPER CAN CUTTING POSITION AND A LOWER CAN RECEIVING POSITION, A MOTOR, MEANS DRIVINGLY CONNECTING SAID MOTOR WITH SAID FEED WHEEL SHAFT, A PIN MEMBER CARRIED BY AND RADIALLY OFFSET FROM SAID FEED WHEEL SHAFT FOR ORBITAL TRAVEL ABOUT SAID SHAFT, A PAWL MEMBER PIVOTALLY CONNECTED WITH SAID FRAME, SAID PAWL MEMBER HAVING A PIN ENGAGEABLE PORTION, AND SAID PIN MEMBER AND PAWL MEMBER SO LOCATED AS TO PRODUCE AN UPWARD THRUST FORCE ON SAID CARRIER MEMBER IN RESPONSE TO ENGAGEMENT OF SAID PIN MEMBER WITH SAID PORTION WHEN SAID CARRIER MEMBER IS BELOW THE SAID CAN CUTTING POSITION. 